WO2013069438A1

WO2013069438A1 - Fixed constant-velocity universal joint

Info

Publication number: WO2013069438A1
Application number: PCT/JP2012/077189
Authority: WO
Inventors: 健太山崎; 博康蛭川
Original assignee: Ntn株式会社
Priority date: 2011-11-11
Filing date: 2012-10-22
Publication date: 2013-05-16
Also published as: JP5964030B2; CN103917797A; JP2013104462A; US9206855B2; EP2778454A4; EP2778454A1; EP2778454B1; US20140243104A1; CN103917797B

Abstract

The track grooves (7) of an outside joint member (2) comprise first track groove parts (7a) located toward the interior and second track groove parts (7b) located toward the opening. The first track groove parts (7a) form arched shapes having a center of curvature which, with respect to the joint center, is offset to the aperture side, and these track groove parts are formed inclined in the circumferential direction with respect to the joint axis line (N-N), with the direction of inclination being in the opposite direction at the adjacent first track groove parts (7a) in the circumferential direction. The second track groove parts (7b) have a different shape than the first track groove parts (7a), in order to increase the effective track length with respect to the maximum operating angle, and are connected to the first track groove parts (7a) closer to the opening side than the joint center (O). When the joint center plane (P) with an operating angle of 0° is taken as the reference, the track grooves (9) of an inside joint member (3) are formed mirror-symmetrical with respect to the track grooves (7) of the outside joint member (2) with which a track-groove pair is formed.

Description

Fixed constant velocity universal joint

The present invention relates to a fixed type constant velocity universal joint, and more particularly, to a fixed type constant velocity universal joint that is used in a power transmission system of an automobile or various industrial machines and allows only angular displacement between two axes of a driving side and a driven side. About.

For example, in a front drive shaft of an automobile, a sliding constant velocity universal joint that allows angular displacement and axial displacement is usually incorporated on the inboard side (differential side), and on the outboard side (wheel side). Incorporates a fixed constant velocity universal joint that allows only angular displacement.

An example of a fixed type constant velocity universal joint used on the outboard side is a longitudinal sectional view of the constant velocity universal joint 101 shown in FIG. 15A in a state where the operating angle is 0 °, and an equivalent velocity universal joint 101 shown in FIG. 15B. A description will be given based on a schematic diagram of a state where the maximum operating angle is taken. The constant velocity universal joint 101 is an eight-ball type Zepper type constant velocity universal joint, and mainly includes an outer joint member 102, an inner joint member 103, a ball 104, and a cage 105. Eight track grooves 107 are formed on the spherical inner peripheral surface 106 of the outer joint member 102 at equal intervals in the circumferential direction and along the axial direction. Track grooves 109 facing the track grooves 107 of the outer joint member 102 are formed on the spherical outer peripheral surface 108 of the inner joint member 103 at equal intervals in the circumferential direction and along the axial direction. A ball 104 is disposed between the

track grooves

107 and 109 that make a pair of the outer joint member 102 and the inner joint member 103 (facing each other in the radial direction). Between the spherical inner peripheral surface 106 of the outer joint member 102 and the spherical outer peripheral surface 108 of the inner joint member 103, a cage 105 that holds the balls 104 at predetermined intervals in the circumferential direction is disposed. The outer periphery of the outer joint member 102 and the outer periphery of the shaft connected to the inner joint member 103 are covered with boots, and grease is enclosed as a lubricant inside the joint (not shown).

As shown in FIG. 15 a, the spherical inner surface 112 of the cage 105 that fits with the spherical inner circumferential surface 106 of the outer joint member 102 and the spherical inner surface of the cage 105 that fits with the spherical outer circumferential surface 108 of the inner joint member 103. The center of curvature of the peripheral surface 113 is formed at the joint center O. In contrast, the curvature center Oo of the ball track center line x of the track groove 107 of the outer joint member 102 and the curvature center Oi of the ball track center line y of the track groove 109 of the inner joint member 103 are relative to the joint center O. Are offset equally on both sides in the axial direction. As a result, when the joint takes an operating angle, the ball 104 is always guided on a plane that bisects the angle formed by the two axes of the outer joint member 102 and the inner joint member 103, and rotates at a constant speed between the two axes. Torque is transmitted.

As shown in FIG. 15 b, the maximum operating angle θmax, which is the main function of the fixed type constant velocity universal joint 101, causes interference between the inlet chamfer 110 provided at the open end (inner peripheral edge) of the outer joint member 102 and the shaft 111. Depends on the angle. The shaft diameter d of the shaft 111 is determined for each joint size in order to ensure an allowable transmission torque. If the entrance chamfer 110 is made large, the length of the track groove 107 (hereinafter referred to as “effective track length”) of the outer joint member 102 with which the ball 104 comes into contact is insufficient, and the ball 104 falls off the track groove 107 and rotates. Torque cannot be transmitted. Therefore, how to set the inlet chamfer 110 while securing the effective track length of the outer joint member 102 is an important factor in securing the operating angle. In the constant velocity universal joint 101 shown in FIGS. 15a and 15b, since the center of curvature Oo of the ball track center line x of the track groove 107 of the outer joint member 102 is offset toward the axial opening side, Advantageously, the maximum operating angle θmax is about 47 °.

In addition, the 8-ball type constant velocity universal joint described above has a smaller track offset, a larger number of balls, and a smaller diameter than the conventional 6-ball type constant velocity universal joint. Lightweight, compact and highly efficient constant velocity universal joints with low torque loss. However, each wedge angle formed between the

track grooves

107 and 109 forming a pair of the outer joint member 102 and the inner joint member 103 in an operating angle of 0 ° is open toward the opening side of the outer joint member 102. Therefore, the

spherical contact portions

106 and 112 of the outer joint member 102 and the cage 105 and the

spherical contact portions

108 and 113 of the inner joint member 103 and the cage 105 are caused by the axial force acting on the ball 104 from the

track grooves

107 and 109. The load that acts on the is generated in a certain direction. Therefore, there is a limit to further increasing efficiency and reducing heat generation.

Therefore, in order to achieve further higher efficiency and lower heat generation, a track groove intersecting type fixed constant velocity universal joint 121 shown in FIGS. 16a and 16b has been proposed (see, for example, Patent Document 1 below). ). FIG. 16A is a longitudinal sectional view of the constant velocity universal joint 121 in a state where the operating angle is 0 °, and FIG. 16B is a schematic diagram showing a state where the constant velocity universal joint 121 has a high operating angle. As shown in FIG. 16a, the constant velocity universal joint 121 mainly includes an outer joint member 122, an inner joint member 123, a ball 124, and a cage 125. Although not shown, the constant velocity universal joint 121 has a plane including the ball track center line x of the eight track grooves 127 of the outer joint member 122 and the joint center O with respect to the joint axis nn. The track grooves 127 are inclined and formed in opposite directions with the track grooves 127 adjacent to each other in the circumferential direction. The ball track center line y of the track groove 129 of the inner joint member 123 is perpendicular to the joint axis nn including the joint center O at the operating angle of 0 ° (including the joint center O at the operating angle of 0 °). The plane is formed in a mirror image symmetry with the ball trajectory center line x of the track groove 127 to be a pair of the outer joint member 122 with respect to the plane (P) extending in the direction of

16A, the track groove 127 formed on the spherical inner peripheral surface 126 of the outer joint member 122 extends in an arc shape along the axial direction, and the center of curvature thereof is located at the joint center O. The track groove 129 formed on the spherical outer peripheral surface 128 of the inner joint member 123 extends in an arc shape along the axial direction, and the center of curvature thereof is located at the joint center O. Balls 124 are interposed at the intersections of the

track grooves

127 and 129 forming a pair of the outer joint member 122 and the inner joint member 123 (opposing in the radial direction). Between the spherical inner peripheral surface 126 of the outer joint member 122 and the spherical outer peripheral surface 128 of the inner joint member 123, a cage 125 that holds the balls 124 at predetermined intervals in the circumferential direction is disposed. The center of curvature of the spherical outer peripheral surface 132 of the cage 125 fitting with the spherical inner peripheral surface 126 of the outer joint member 122 and the spherical inner peripheral surface 133 of the cage 125 fitting with the spherical outer peripheral surface 128 of the inner joint member 123 are , Both are formed at the joint center O. In this constant velocity universal joint 121, as described above, the center of curvature of the ball track center lines x and y of the paired

track grooves

127 and 129 is not offset in the axial direction with respect to the joint center O, but forms a pair. The track grooves 127 and 129 intersect, and the ball 124 is interposed at the intersecting portion. Thereby, when the joint takes an operating angle, the ball 124 is always guided on a plane that bisects the angle formed by both the outer joint member 122 and the inner joint member 123, and rotates at a constant speed between the two axes. Torque is transmitted.

In the track groove crossing type fixed constant velocity universal joint 121 described above, the

track grooves

127 and 129 of the

joint members

122 and 123 are adjacent to each other in the circumferential direction and are inclined in opposite directions. A force in the opposite direction from the ball 124 acts on the pocket portion 125 a adjacent to the circumferential direction of the cage 125. The cage 125 is stabilized at the joint center O position by the forces in the opposite directions. Therefore, the contact force between the spherical outer circumferential surface 132 of the cage 125 and the spherical inner circumferential surface 126 of the outer joint member 122 and the contact between the spherical inner circumferential surface 133 of the cage 125 and the spherical outer circumferential surface 128 of the inner joint member 123. Force is suppressed. As a result, the joint operates smoothly during high loads and high-speed rotation, so torque loss and heat generation are suppressed, and durability is improved.

JP 2009-250365 A

Although the above-described track groove intersection type fixed constant velocity universal joint 121 is excellent as a low heat generation joint, as shown in FIG. 16B, when the inlet chamfer 130 of the outer joint member 122 is enlarged, the curvature of the track groove 127 is increased. Due to the structure in which the center coincides with the joint center O, the effective track length of the track groove 127 of the outer joint member 122 is insufficient, and the ball 124 drops off from the track groove 127 when the high operating angle θ is taken. There is a problem that the operating angle cannot be achieved.

Therefore, the inventors of the present application have studied to provide a linear portion in the track groove of both joint members in order to increase the operating angle of the above-described fixed constant velocity universal joint of the track groove intersection type. A longitudinal sectional view and a front view of the constant velocity universal joint are shown in FIGS. 12a and 12b, respectively. As shown in FIG. 12a, in this constant velocity universal joint 141, the track groove 147 of the outer joint member 142 includes a joint center O in a state where the operating angle is 0 °, and is a plane (joint joint) perpendicular to the joint axis nn. The back side and the opening side with respect to the center plane) are arc-shaped track grooves 147a and linear track grooves 147b with the joint center O as the center of curvature, respectively. On the other hand, the track groove 149 of the inner joint member 143 has an arcuate track groove 149a and a straight track groove 149b with the joint center O as the center of curvature at the opening side and the back side of the joint center plane, respectively. It is what.

As shown in FIG. 12b, the

track grooves

147 and 149 are inclined in the circumferential direction with respect to the joint axis line, and the inclination directions are adjacent to each other in the

track grooves

147A, 147B and 149A and 149B adjacent to each other in the circumferential direction. It is formed in the opposite direction. Balls 144 are disposed at the intersections of the

track grooves

147A, 149A and 147B, 149B forming a pair of the outer joint member 142 and the inner joint member 143. Therefore, when the

joint members

142 and 143 rotate relative to each other at an operating angle of 0 ° as shown in the figure, the wedge angle formed between the

track grooves

147A and 149A and the direction between the opening 147B and 149B are formed. The direction in which the wedge angle opens is opposite to each other, and a force in a direction opposite to the ball 144 acts on the pocket portion 145a adjacent to the circumferential direction of the cage 145, so that the cage 145 is stable at the joint center O position. To do. Therefore, the contact force between the spherical outer circumferential surface 152 of the cage 145 and the spherical inner circumferential surface 146 of the outer joint member 142 and the contact between the spherical inner circumferential surface 153 of the cage 145 and the spherical outer circumferential surface 148 of the inner joint member 143. As a result of the force being suppressed and the operability of the joint being improved, torque loss and heat generation are suppressed, and durability is improved.

As described above, in the track groove 147 of the outer joint member 142, if the linear track groove 147b is formed in the opening side region from the joint center plane, the effective track length is increased to increase the operating angle. be able to. However, it has been found that the above-described configuration has a problem in terms of suppressing torque loss and heat generation of the joint when an operating angle with a high frequency of use is taken. The reason for this will be described with reference to FIG.

Since the

track grooves

147 and 149 and the ball 144 are normally in contact with each other at a contact angle (about 30 ° to 45 °), the

track grooves

147 and 149 and the ball 144 are connected to each other as shown in FIG. The

track grooves

147 and 149 are in contact with each other at a position indicated by a broken line on the side surface side of the

track grooves

147 and 149 slightly apart from the groove bottom of 149. When the joint takes an operating angle, each ball 144 has a wedge angle component (not shown) due to the intersection of the

track grooves

147 and 149 and a wedge angle due to the joint radial expansion between the groove bottoms of the

track grooves

147 and 149. Both components α act. Among them, with respect to the wedge angle component due to the intersection of the

track grooves

147 and 149, since the inclination directions of the

track grooves

147 and 149 are opposite to each other, the force in the direction opposite to the pocket portion 145 a of the cage 145 from the ball 144. Will cancel each other out and balance the force.

However, as shown in FIG. 13, the wedge angle component α due to the joint radial expansion between the groove bottoms of the

track grooves

147 and 149 is in the phase ranges of 0 ° to 90 ° and 270 ° to 360 ° in FIG. Is located between the

linear track grooves

147b and 149b, and a force toward the opening acts on the ball 144 in this phase range due to the wedge angle component α1 that opens toward the opening. On the other hand, since the ball 144 in the phase range of 90 ° to 270 ° is positioned between the arc-shaped

track grooves

147a and 149a, the ball in this phase range has a wedge angle component α2 generated by the radial expansion of the joint. 0, and the pushing force of the ball 144 is not generated. Therefore, when the wedge angle component due to the intersection of the

track grooves

147 and 149 and the wedge angle component α due to the joint radial expansion between the groove bottoms of the

track grooves

147 and 149 are combined with each ball 144, the cage 145 is obtained. The forces acting from the balls 144 on the respective pocket portions 145a are not balanced, the contact force between the spherical outer circumferential surface 152 of the cage 145 and the spherical inner circumferential surface 146 of the outer joint member 142, and the spherical inner circumferential surface 153 of the cage 145. And the contact force between the outer peripheral surface 148 of the inner joint member 143 cannot be reduced. In particular, it has been found that there is a significant problem in terms of torque loss and suppression of heat generation in the range of operating angles that are frequently used, including normal angles.

In view of the above circumstances, it is an object of the present invention to provide a fixed type constant velocity universal joint capable of taking a high operating angle while having low torque loss and heat generation, high efficiency and excellent durability. To do.

As a result of various studies to achieve the above-mentioned object, the inventors of the present application have found that each of the outer joint member and the inner joint member has a track groove in order to improve efficiency by reducing torque loss and heat generation. An arc-shaped first track groove portion that can form an intersecting portion (intersecting track) in cooperation with the side is provided to cover a range of frequently used operating angles, and each of the track grooves of both joint members has a first The present inventors have arrived at a novel idea of providing a second track groove portion having a shape different from that of the one track groove portion to cover a range of a high operating angle that is less frequently used. In addition to this, the idea is to offset the center of curvature of the arc-shaped first track groove portion to the opening side with respect to the joint center in order to increase the effective track length with respect to the maximum operating angle and to increase the operating angle. did.

The present invention created to achieve the above object includes an outer joint member having a plurality of track grooves extending in the axial direction on a spherical inner peripheral surface and having an opening side and a back side spaced apart in the axial direction, and a spherical shape. Torque is transmitted by interposing between the outer joint member track groove and the inner joint member track groove formed on the outer peripheral surface with a plurality of track grooves paired with the outer joint member track groove. A fixed type comprising a plurality of balls and a cage having a spherical outer peripheral surface and a spherical inner peripheral surface that hold the balls and fit to the spherical inner peripheral surface of the outer joint member and the spherical outer peripheral surface of the inner joint member, respectively. In the constant velocity universal joint, the track groove of the outer joint member includes a first track groove portion located on the back side and a second track groove portion located on the opening side, and the first track groove portion is located on the opening side with respect to the joint center. Offset A circular arc shape having a center of curvature at the position and is inclined in the circumferential direction with respect to the axis of the joint, and the inclined directions are formed in opposite directions in the first track groove portions adjacent to each other in the circumferential direction. The track groove portion has a different shape from the first track groove portion in order to increase the effective track length with respect to the maximum operating angle, and is connected to the first track groove portion on the opening side from the joint center. The groove is characterized in that it is formed mirror-symmetrically with the track groove that forms a pair of the outer joint member with reference to the joint center plane in the state where the operating angle is 0 °. Here, the “joint axis” means a longitudinal axis serving as the center of rotation of the joint, and indicates a joint axis NN in an embodiment described later. Strictly speaking, the “joint center plane in a state where the operating angle is 0 °” is a plane including the joint center and extending in a direction orthogonal to the axis of the joint in a state where the operating angle is 0 °.

In the present invention, in the track groove of the outer joint member, the second track groove portion for increasing the effective track length provided on the opening side is connected to the first track groove portion on the opening side from the joint center (inner joint joint). In the track groove of the member, the second track groove portion provided on the back side is connected to the first track groove portion on the back side from the joint center). That is, in the fixed type constant velocity universal joint according to the present invention, the formation of the first track groove portion that forms a cross track excellent in the effect of suppressing torque loss or the like as compared with the constant velocity universal joint 141 shown in FIG. It means that the range is expanded. Therefore, high efficiency can be achieved by suppressing torque loss and heat generation in the normal operating angle range. On the other hand, since the arc-shaped first track groove portion has a center of curvature that is offset toward the opening side with respect to the joint center, this offset amount is effective in suppressing torque loss and the like obtained by adopting the above-described configuration. By appropriately adjusting within a range where (the efficiency of the joint) is not impaired, it is possible to effectively increase the length of the second track groove portion (effective track length) and increase the operating angle. Therefore, according to the present invention, it is possible to realize a fixed type constant velocity universal joint that can take a high operating angle while having low torque loss and heat generation, high efficiency, and excellent durability.

When the angle formed by the straight line connecting the point where the first track groove portion and the second track groove portion are connected to the joint center with respect to the joint center plane in the state where the operating angle is 0 ° is β, this angle β is used. By appropriately setting according to the above, high efficiency of the fixed type constant velocity universal joint can be appropriately realized. In particular, considering the normal operating angle range of the constant velocity universal joint for automobiles, the angle β can be set to 3 to 10 ° to be widely used for various types of vehicles. Here, the angle β is defined as the smallest angle formed by the straight line on the joint center plane when the operating angle is 0 °.

As long as the center of curvature of the first track groove is offset toward the opening with respect to the joint center, the position in the radial direction can be arbitrarily set. That is, the center of curvature of the first track groove portion may be disposed on an inclined axis N′-N ′ inclined in the circumferential direction with respect to the joint axis NN (see FIG. 4 and FIG. 5). Further, it may be arranged at a position offset in the radial direction with respect to the tilt axis N′-N ′ (see FIG. 10). When the center of curvature of the first track groove is offset in the radial direction with respect to the axis of the joint, the track groove depth on the back side of the joint can be adjusted according to the offset amount, so that the optimal track It becomes possible to ensure the groove depth.

Place the center of curvature of the spherical outer peripheral surface of the cage at a position offset to the opening side with respect to the joint center, and position the center of curvature of the spherical inner peripheral surface of the cage to the back side with respect to the joint center. Can be arranged. In this way, the thickness of the cage can be gradually increased toward the opening side, so that the strength of the cage can be secured particularly at a high operating angle, and the reliability of the joint can be improved.

The second track groove portion may have an arc-shaped portion having a center of curvature at a position that is radially outward of the first track groove portion and offset toward the opening side from the joint center. As a result, the effective track length can be increased to increase the maximum operating angle. In this case, the second track groove portion includes only the arc-shaped portion described above, and the arc-shaped portion may be smoothly connected to the first track groove portion, or may include the arc-shaped portion and the linear portion. Thus, the linear portion may be smoothly connected to the first track groove portion.

It is desirable that the number of torque transmission balls is 8, 10, or 12. In this way, it is possible to realize a fixed type constant velocity universal joint that is lightweight, compact, highly efficient, and capable of obtaining a high operating angle, and thus a drive shaft of an automobile.

According to the present invention, it is possible to realize a compact fixed type constant velocity universal joint capable of taking a high operating angle while having low torque loss and heat generation, high efficiency and excellent durability.

It is a fragmentary longitudinal cross-sectional view of the fixed type constant velocity universal joint which concerns on 1st Embodiment of this invention. It is a front view of the fixed type constant velocity universal joint which concerns on 1st Embodiment of this invention. It is a partial longitudinal cross-sectional view of an outer joint member. It is a front view of an outer joint member. It is a rear view of an inner joint member. It is a side view of an inner joint member. It is a front view of an inner joint member. It is a fragmentary longitudinal cross-section which shows the detail of the track groove of an outer joint member. It is a longitudinal cross-sectional view which shows the detail of the track groove of an inner side coupling member. It is a schematic diagram which shows the state which the constant velocity universal joint shown in FIG. 1 took the maximum operating angle. It is a schematic diagram which shows the state which the constant velocity universal joint shown in FIG. 14 took the maximum operating angle. It is a perspective view of an outside joint member. It is a perspective view of an inner joint member. It is a figure which shows an example of the drive shaft for motor vehicles in which the fixed type constant velocity universal joint shown in FIG. 1 was integrated. It is a longitudinal cross-sectional view of the outer joint member used with the fixed type constant velocity universal joint which concerns on 2nd Embodiment of this invention. It is a longitudinal cross-sectional view of the outer joint member used with the fixed type constant velocity universal joint which concerns on 3rd Embodiment of this invention. It is a fragmentary longitudinal cross-sectional view of the holder | retainer used with the fixed type constant velocity universal joint which concerns on 4th Embodiment of this invention. It is the fragmentary longitudinal cross-section of the fixed type constant velocity universal joint examined in the process leading to the present invention. It is a right view of the fixed type constant velocity universal joint examined in the process leading to the present invention. It is a fragmentary sectional view showing the state where the fixed type constant velocity universal joint shown in Drawing 12a took an operating angle, and is a figure explaining the technical knowledge in the process leading to the present invention. It is a figure explaining the technical knowledge in the process leading to the present invention. It is a longitudinal cross-sectional view of the conventional fixed type constant velocity universal joint. It is a schematic diagram which shows the state which the fixed type constant velocity universal joint shown to FIG. 15a took the maximum operating angle. It is a longitudinal cross-sectional view of the conventional fixed type constant velocity universal joint. It is a schematic diagram which shows the state which the fixed type constant velocity universal joint shown to FIG. 16a took the high operating angle.

Embodiments of the present invention will be described with reference to the drawings.

FIG. 1a shows a partial longitudinal sectional view of a fixed type constant velocity universal joint 1 (hereinafter also simply referred to as “constant velocity universal joint 1”) according to the first embodiment of the present invention, and FIG. The front view when seen from the opening side is shown. The constant velocity universal joint 1 is classified as a track groove intersection type, and mainly includes an outer joint member 2, an inner joint member 3, a ball 4 and a cage 5. As shown in FIG. 2, eight track grooves 7 extending in the axial direction are formed on the spherical inner peripheral surface 6 of the outer joint member 2, and each track groove 7 is formed with respect to the joint axis NN. Thus, the angle γ is inclined in the circumferential direction, and the inclined direction is formed in opposite directions by the track grooves 7 (7A, 7B) adjacent in the circumferential direction. Further, as shown in FIG. 3, eight track grooves 9 extending in the axial direction are formed on the spherical outer peripheral surface 8 of the inner joint member 3, and each track groove 9 extends along the joint axis NN. On the other hand, the angle γ is inclined in the circumferential direction, and the inclined direction is formed in opposite directions by the track grooves 9 (9A, 9B) adjacent in the circumferential direction. Then, the balls 4 are respectively arranged at the intersections of the

track grooves

7 and 9 forming a pair of the outer joint member 2 and the inner joint member 3. Details of the track grooves 7 (7A, 7B) of the outer joint member 2 and the track grooves 9 (9A, 9B) of the inner joint member 3 will be described later.

Here, the term “ball trajectory centerline” is used in the following to accurately indicate the form (inclined state, curved state, etc.) and shape of the

track grooves

7 and 9. The center line of the ball trajectory means a locus drawn by the center of the ball 4 when the ball 4 interposed between the pair of

track grooves

7 and 9 moves along the

track grooves

7 and 9. Accordingly, the inclined state and the curved state of the

track grooves

7 and 9 are the same as the inclined state and the curved state of the ball track center line.

The track groove 7 of the outer joint member 2 has a ball track line X. More specifically, the track groove 7 is provided on the back side, and an arc-shaped ball trajectory center line Xa having a center of curvature at a point Oo1 offset from the joint center O by the dimension f1 (see FIG. 4) on the opening side. The first track groove portion 7a is provided on the opening side, and the second track groove portion 7b has an arc-shaped ball trajectory center line Xb curved in the opposite direction to the first track groove portion 7a. That is, the second track groove portion 7b of the present embodiment is composed of only an arc-shaped portion having a shape different from that of the first track groove portion 7a (curved in the opposite direction), and the ball track center line Xb (the back end portion thereof). Are smoothly connected to the opening side end of the ball track center line Xa of the first track groove 7a. Further, the offset point Oo1, which is the center of curvature of the first track groove portion 7a, is an inclined axis N′-N ′ inclined with respect to the joint axis NN by an angle γ (see FIG. 4; however, regarding the angle γ 2) and is not radially offset with respect to the joint center O.

Referring to the partial longitudinal sectional view of the outer joint member 2 shown in FIGS. 2a and 2b and the front view (right side view) seen from the opening side, the track groove 7 of the outer joint member 2 is connected to the joint axis NN. In the following, the state of being inclined by the angle γ in the circumferential direction will be described in detail. The track grooves 7 of the outer joint member 2 are given the reference numerals of the

track grooves

7A and 7B due to the difference in the inclination direction. As shown in FIG. 2a, the plane M including the ball track center line X and the joint center O of the track groove 7A is inclined by an angle γ with respect to the joint axis NN. Although not shown, the track groove 7B adjacent to the track groove 7A in the circumferential direction is inclined by an angle γ with respect to the joint axis NN in the direction opposite to the inclination direction of the track groove 7A. . In this embodiment, the entire area of the ball track center line X of the track groove 7A (and 7B), that is, both the ball track center line Xa of the first track groove portion 7a and the ball track center line Xb of the second track groove portion 7b are flat. It is formed on M. However, the present invention is not limited to this, and a mode in which only the ball trajectory center line Xa of the first track groove portion 7a is included in the plane M can also be adopted. Therefore, a plane M including at least the ball track center line Xa of the first track groove 7a and the joint center O is inclined by an angle γ in the circumferential direction with respect to the joint axis NN, and the inclined direction is in the circumferential direction. The adjacent first track groove portions 7a may be formed in opposite directions.

Suppose here that the track groove codes are supplemented. When referring to the entire track groove of the outer joint member 2, reference numeral 7 is attached, and

reference numerals

7a and 7b are attached to the first and second track groove portions, respectively. Further, in order to distinguish track grooves having different inclination directions,

reference numerals

7A and 7B are given, reference numerals 7Aa and 7Ba are assigned to the first track groove portions of the

track grooves

7A and 7B, and second tracks of the

track grooves

7A and 7B are given. Reference numerals 7Ab and 7Bb are attached to the grooves, respectively. The same applies to the track grooves 9 of the inner joint member 3 described in detail below.

The track groove 9 of the inner joint member 3 has a ball track center line Y. More specifically, the track groove 9 has a first track groove portion 9a having an arc-shaped ball trajectory center line Ya centered on a point Oi1 offset by a dimension f1 (see FIG. 5) on the back side with respect to the joint center O. And a second track groove portion 9b having an arcuate ball trajectory center line Yb which is provided on the back side and is curved in a direction opposite to the first track groove portion 9a. That is, the second track groove portion 9b of the present embodiment is composed of only an arc-shaped portion having a different shape (curved in the opposite direction) from the first track groove portion 9a, and the opening side end portion of the ball trajectory center line Yb is The first track groove 9a is smoothly connected to the back end of the ball track center line Ya. Further, the offset point Oi1 that is the center of curvature of the first track groove portion 9a is an inclined axis N′-N ′ inclined with respect to the joint axis NN by an angle γ (see FIG. 5; (See FIG. 3b) and is not offset radially relative to the joint center O.

Referring to the rear view, side view, and front view of the inner joint member 3 shown in FIGS. 3a to 3c, the track groove 9 of the inner joint member 3 is inclined in the circumferential direction with respect to the joint axis NN. The state of being present will be described in detail. The track grooves 9 of the inner joint member 3 are given the reference numerals of the

track grooves

9A and 9B because of the difference in the inclination direction. As shown in FIG. 3b, the plane Q including the ball track center line Y and the joint center O of the track groove 9A is inclined by an angle γ with respect to the joint axis NN. Although not shown, the track groove 9B adjacent to the track groove 9A in the circumferential direction has a plane Q including the ball track center line Y and the joint center O of the track groove 9B with respect to the joint axis NN. The track groove 9A is inclined by an angle γ in the direction opposite to the inclination direction of the track groove 9A. The inclination angle γ with respect to the joint axis NN of the plane Q (and the plane M described above) takes into consideration the operability of the constant velocity universal joint 1 and the spherical width F of the inner joint member 3 on the closest side of the track groove 9. In addition, the angle is preferably 4 ° to 12 °. Further, like the outer joint member 2 described above, in the present embodiment, the entire region of the ball track center line Y of the track groove 9A, that is, the ball track center line Ya of the first track groove portion 9a and the ball track of the second track groove portion 9b. Both center lines Yb are formed on the plane Q. However, the present invention is not limited to this, and a mode in which only the ball trajectory center line Ya of the first track groove portion 9a is included in the plane Q can also be implemented. Accordingly, the plane Q including at least the ball track center line Ya of the first track groove 9a and the joint center O is inclined in the circumferential direction with respect to the joint axis NN, and the inclined direction is adjacent to the first track in the circumferential direction. It suffices if the grooves 9a are formed in opposite directions.

From the above configuration, the ball track center line Y of the track groove 9 of the inner joint member 3 is based on the joint center plane P in a state where the operating angle is 0 °. It is formed mirror-symmetric with the center line X. Although not shown, the cross-sectional shapes of the

track grooves

7 and 9 of both

joint members

2 and 3 are formed in an elliptical shape or a Gothic arch shape, and the

track grooves

7 and 9 and the ball 4 are 30 ° to 45 °. It is a so-called angular contact that makes contact with a contact angle of about °. Therefore, the ball 4 is in contact with the

track grooves

7 and 9 on the side surface side of the

track grooves

7 and 9 that are slightly apart from the groove bottoms of the

track grooves

7 and 9.

Next, details of the track grooves as seen from the longitudinal section of the outer joint member 2 will be described based on the partial longitudinal sectional view of the outer joint member 2 shown in FIG. 4 is a cross-sectional view of the track groove 7A shown in FIG. 2A as viewed on a plane M including the ball trajectory center line X and the joint center O. FIG. Accordingly, FIG. 4 is not strictly a longitudinal sectional view in the plane including the joint axis NN, but in the plane including the inclined axis N′-N ′ inclined by the angle γ with respect to the joint axis NN. A longitudinal section is shown. 4 shows only the track groove 7A of the outer joint member 2, the track groove 7B is merely inclined in the direction opposite to the track groove 7A, and other configurations are the same as the track groove 7A. Therefore, the detailed description shown in the figure is omitted.

On the spherical inner peripheral surface 6 of the outer joint member 2, a track groove 7A having a ball track center line X is formed along the axial direction. The track groove 7A includes a first track groove portion 7Aa having an arc-shaped ball trajectory center line Xa having a center of curvature at a point Oo1 offset by a dimension f1 on the opening side with respect to the joint center O, and the first track groove portion 7Aa. Arc-shaped ball trajectory center line Xb curved in the opposite direction, more specifically, an arc-shaped ball centered on a point Oo2 radially outside the first track groove 7Aa and having a larger offset amount than the offset point Oo1. And a second track groove portion 7Ab having a ball track center line Xb. That is, the second track groove portion 7Aa is composed only of an arc-shaped portion, and the back end portion of the ball track center line Xb is the opening side end portion A (both offset points Oo1 of the ball track center line Xa of the first track groove portion 7Aa. , Oo2 and the point where the straight line L1 of the track groove 7A intersects the ball trajectory center line X). When a straight line connecting the opening side end A of the first track groove portion 7Aa and the joint center O is L2, the plane M including the straight line L2, the ball track center line X of the track groove 7A and the joint center O (FIG. 2a). Reference) The plane including the angle β ′ formed by the perpendicular K at the joint center O of the joint axis N′-N ′ projected above is inclined by the angle γ with respect to the joint axis NN. The perpendicular line K is on the joint center plane P with an operating angle of 0 °. Therefore, the angle β formed with respect to the joint center plane P in a state where the straight line L2 has an operating angle of 0 ° has a relationship of sin β = sin β ′ × cos γ. In the present embodiment, the first track groove portion 7Aa and the second track groove portion 7Ab of the outer joint member 2 are each formed by a single arc-shaped portion. However, the present invention is not limited to this, and the track groove depth and the like are considered. And may be formed of a plurality of arc-shaped portions.

Similarly, the details of the track groove will be described from the longitudinal section of the inner joint member 3 based on FIG. FIG. 5 is a cross-sectional view of the track groove 9A of FIG. Therefore, strictly speaking, FIG. 5 is not a longitudinal sectional view in a plane including the joint axis NN but is inclined axis N ′ inclined by an angle γ with respect to the joint axis NN, as in FIG. A cross section in a plane including -N 'is shown. Further, FIG. 5 shows only the track groove 9A of the inner joint member 3, but the track groove 9B is merely inclined in the opposite direction to the track groove 9A, and other configurations are the same as the track groove 9A. Therefore, the detailed description shown in the figure is omitted.

On the spherical outer peripheral surface 8 of the inner joint member 3, a track groove 9A having a ball track center line Y is formed along the axial direction. The track groove 9A includes a first track groove portion 9Aa having an arc-shaped ball trajectory center line Ya whose center of curvature is a point Oi1 offset from the joint center O by a dimension f1 on the back side, and the first track groove portion 9Aa. More specifically, an arc-shaped ball trajectory centered at a point Oi2 that is radially outward of the ball trajectory centerline Ya of the first track groove 9Aa and that has a larger offset amount than the offset point Oi1. And a second track groove 9Ab having a center line Yb. That is, the second track groove portion 9Ab consists of only an arc-shaped portion, and the opening side end portion of the ball track center line Yb is the back end portion B (both offset points Oi1) of the ball track center line Ya of the first track groove portion 9Aa. , Oi2 and the point where the straight line R1 of the track groove 9A intersects the ball trajectory center line Y). When a straight line connecting the back end B of the first track groove portion 9Aa and the joint center O is R2, the plane Q including the straight line R2, the ball track center line Y of the track groove 9A and the joint center O (FIG. 3b). Reference) The plane including the angle β ′ formed by the perpendicular K at the joint center O of the joint axis N′-N ′ projected above is inclined by the angle γ with respect to the joint axis NN. The perpendicular line K is on the joint center plane P with an operating angle of 0 °. Accordingly, the angle β formed with respect to the joint center plane P in a state where the straight line R2 has an operating angle of 0 ° has a relationship of sin β = sin β ′ × cos γ. In the present embodiment, the first track groove portion 9Aa and the second track groove portion 9Ab of the inner joint member 3 are each formed by a single arc-shaped portion, but both the track groove portions 9Aa and 9Ab are formed by the outer joint member 2 described above. Similarly to the track groove, each may be formed by a plurality of arcs in consideration of the track groove depth and the like.

Next, an angle β formed by the straight lines L2 and R2 with respect to the joint center plane P in a state where the operating angle is 0 ° will be described. When the operating angle θ is taken, the ball 4 moves by θ / 2 with respect to the plane P of the outer joint member 2 and the inner joint member 3. The angle β is determined from ½ of the frequently used operating angle, and the range of the track groove with which the ball 4 contacts is determined within the frequently used operating angle range. Here, the operating angle that is frequently used is defined. First, the common angle of the joint refers to an operating angle generated in a fixed type constant velocity universal joint of the front drive shaft when the steering is in a straight traveling state in an automobile when one person rides on a horizontal and flat road surface. The service angle is usually selected and determined between 2 ° and 15 ° according to the design conditions for each vehicle type. The frequently used operating angle is not the high operating angle that occurs when the above-mentioned automobile is turned right or left at an intersection, for example, but the operating angle that occurs in a fixed constant velocity universal joint on a curved road that runs continuously This is also determined according to the design conditions for each vehicle type. The operating angle that is frequently used is targeted at a maximum of 20 °. Thus, the angle β formed by the straight lines L2 and R2 with respect to the joint center plane P in the state where the operating angle is 0 ° is set to 3 ° to 10 °. However, the angle β is not limited to 3 ° to 10 °, and can be appropriately set according to the design conditions of the vehicle type. By setting the angle β to 3 ° to 10 °, it can be used for various types of vehicles.

4, the opening-side end A of the ball track center line Xa of the first track groove 7Aa in FIG. 4 is the ball when moved to the most opening side along the axial direction when the operating angle is frequently used. 4 becomes the center position. Similarly, in the inner joint member 3, in FIG. 5, the rear end B of the ball track center line Ya of the first track groove 9 </ b> Aa has moved to the innermost side along the axial direction when the operating angle is frequently used. Becomes the center position of the ball 4 at the time. Since it is set in this way, in the range of operating angles where the frequency of use is high, the ball 4 has the first track groove portions 7Aa and 9Aa of the outer joint member 2 and the inner joint member 3, and the inclination direction is opposite to these. It is located within the range of the first track grooves 7Ba and 9Ba (see FIGS. 2 and 3), that is, within the range of the intersecting track.

In this case, since forces in opposite directions from the balls 4 act on the pockets 5a adjacent to the circumferential direction of the cage 5, the centers of curvature of the

first track grooves

7a, 9a of the

joint members

2, 3 are the joint center O. The cage 5 is stabilized at the position of the joint center O. If the cage 5 is stabilized at the position of the joint center O, the contact force between the spherical outer circumferential surface 12 of the cage 5 and the spherical inner circumferential surface 6 of the outer joint member 2, and the spherical inner circumferential surface 13 of the cage 5 and the inner side The contact force with the spherical outer peripheral surface 8 of the joint member 3 is suppressed to the maximum, and the smooth operability of the joint at the time of high load and high speed rotation is ensured. Therefore, torque loss and heat generation are effectively suppressed. High efficiency can be achieved.

However, when the second track groove portion 7b having a shape different from that of the first track groove portion 7a is provided on the opening side of the track groove 7 of the outer joint member 2 in order to increase the effective track length and increase the operating angle. (Especially when the arc-shaped second track groove portion 7b curved in the direction opposite to the first track groove portion 7a is provided as in the present embodiment), the first

track groove portions

7a, 9a of the

joint members

2, 3 are provided. If the center of curvature is arranged at the joint center O, there is a restriction on further increasing the operating angle. The reason will be described in detail with reference to FIG.

FIG. 14 shows that the first track groove portion 7Aa ′ having an arc-shaped ball trajectory center line Xa ′ with the joint center O as the center of curvature is curved in the opposite direction to the first track groove portion 7Aa ′ on the spherical inner peripheral surface. A track groove comprising a second track groove portion 7Ab ′ having an arc-shaped ball track center line Xb ′ smoothly connected to the opening side end portion A ′ of the first track groove portion 7Aa ′ (ball track center line Xa ′). It is principal part sectional drawing of the outer joint member in which 7A 'was formed. The position (angle β ′) of the opening-side end A ′ of the first track groove 7Aa ′ is the same as that of the outer joint member 2 constituting the constant velocity universal joint 1 according to the first embodiment of the present invention described above. is there. Although not shown, the outer joint member 2 'that forms a pair on the inner periphery of the outer joint member 2' shown in FIG. 14 on the spherical outer peripheral surface with reference to the joint center plane P at an operating angle of 0 °. An inner joint member in which a track groove that is mirror-imaged with the 'track groove 7A' is provided.

In this case, in order to increase the effective track length, it is effective to reduce the length of the second track groove portion 7Ab ′ of the outer joint member 2 ′, more specifically, the radius of curvature of the second track groove portion 7Ab ′ as much as possible. Become. That is, assuming that the angle of the inlet chamfer 10 provided at the opening end of the outer joint member 2 ′ is fixed, the center of curvature of the second track groove portion 7Ab ′ (ball track center line Xb ′) is shown in FIG. In the case where the second track groove portion 7Ab ′ is disposed at the offset point Oox1, the length (effective track length) of the second track groove portion 7Ab ′ can be increased as compared with the case where it is disposed at the offset point Oox2 in FIG. However, the smaller the radius of curvature of the second track groove portion 7Ab 'is, the more the joint has a higher operating angle, the more the track groove 7A' of the outer joint member 2 'and the inner joint member paired therewith. Since the wedge angle formed with the track groove increases and the force pushing the ball toward the opening increases, the load generated in the pocket portion 5a of the cage 5 increases, and the durability and strength of the joint are increased. descend.

In order to prevent such a problem from occurring as much as possible, in the present invention, as described above, the point Oo1 where the center of curvature of the first track groove portion 7a of the outer joint member 2 is offset from the joint center O to the opening side. It was decided to be located at. In this way, as long as the design conditions other than the center of curvature of the first track groove portion are the same, the case where the present invention shown in FIG. 6a is applied is the one shown in FIG. 6b (the outer joint member 2 ′ The center of curvature of the first track groove portion 7Aa ′ is located at the joint center O and has the same structure as that shown in FIG. (Refer to the position of the offset point Oo2 serving as the center of curvature of the second track groove portion 7Ab shown in FIG. 6a and the position of the offset point Oo2 ′ serving as the center of curvature of the second track groove portion 7Ab ′ shown in FIG. 6b). Therefore, the track margin can be increased. Here, the “track margin” means the track groove 7 (7 ′ of the ball 4 and the outer joint member 2 (2 ′) when the joint takes an operating angle (maximum operating angle in FIGS. 6a and 6b) θ. ) To the edge of the inlet chamfer 10 of the outer joint member 2 (2 ′). More specifically, it is the distance from the contact point Cp to the intersection of the locus of the contact point and the edge of the entrance chamfer 10. Therefore, it can be said that the larger this is, the more difficult the ball is to drop off from the track groove, which is advantageous in increasing the maximum operating angle of the joint.

In addition, the track margin will be explained in more detail. When the joint takes the maximum operating angle θ, as shown in FIGS. 6a and 6b, the straight line connecting the center point Ob of the ball 4 and the joint center O is inclined by θ / 2 with respect to the joint center plane P. . At this time, the dimension z from the contact point Cp between the ball and the track groove to the edge of the entrance chamfer 10 is the track margin, and the embodiment of the present invention shown in FIG. 6a is compared with the comparison shown in FIG. 6b. Compared to the target, the track margin (dimension z) is increased.

Accordingly, an arc-shaped ball track center line curved to the opposite side of the ball track center line Xa of the first track groove portion 7a (7Aa, 7Ba) on the opening side of the track groove 7 (7A, 7B) of the outer joint member 2. If the second track groove portion 7b (7Ab, 7Bb) having Xb is provided and the center of curvature of the first track groove portion 7a (7Aa, 7Ba) is positioned at the point Oo1 offset from the joint center O to the opening side, A large track margin can be secured to increase the maximum operating angle of the joint.

As the amount of offset of the first

track groove portions

7a and 9a with respect to the joint center O with respect to the curvature increases, the effect of suppressing torque loss and heat generation decreases (the efficiency of the joint decreases). If the offset amount of the first

track groove portions

7a, 9a is adjusted so that the suppression effect is not excessively reduced, the effect of suppressing torque loss and the like due to the use of the joint common angle range, which is frequently used, is covered with the cross track structure. In this case, the first

track groove portions

7a and 9a exceed the negative portion obtained by offsetting the centers of curvature in the axial direction with respect to the joint center O. In addition, due to the structure of the constant velocity universal joint 1 according to the present invention, the balls 4 arranged in the circumferential direction are temporarily divided into the first track groove portion and the second track groove portion in the range of the high operating angle. . Accordingly, the force acting from the balls 4 on the pockets 5a of the cage 5 is not balanced, and the contact portion between the spherical outer circumferential surface 12 of the cage 5 and the spherical inner circumferential surface 6 of the outer joint member 2, and the cage Although a contact force is generated at the contact portion between the spherical inner peripheral surface 13 of the inner surface 5 and the spherical outer peripheral surface 8 of the inner joint member 3, the range of high operating angles is less frequently used. Therefore, the constant velocity universal joint 1 according to the present invention can effectively suppress torque loss and heat generation as compared with the constant velocity universal joint 141 shown in FIG. From the above, according to the present invention, it is possible to realize a fixed type constant velocity universal joint capable of taking a high operating angle while having high efficiency and low durability with little torque loss and heat generation. .

In the constant velocity universal joint 1 of the present embodiment, the clearance between the pocket portion 5a of the cage 5 and the ball 4 may be set as a clearance. In this case, the clearance width of the clearance is preferably set to about 0 to 40 μm. By setting the clearance, the ball 4 held in the pocket portion 5a of the cage 5 can be operated smoothly, and torque loss can be further reduced.

7a and 7b show perspective views of the outer joint member 2 and the inner joint member 3 which are constituent members of the constant velocity universal joint 1 described above. This perspective view three-dimensionally shows the track grooves described so far. As shown in FIG. 7a,

track grooves

7A and 7B inclined in the circumferential direction with respect to the joint axis NN (not shown) are alternately formed on the spherical inner peripheral surface 6 of the outer joint member 2, and the track The inclination directions of the

grooves

7A and 7B are opposite to each other. The

track grooves

7A and 7B are composed of first track groove portions 7Aa and 7Ba and second track groove portions 7Ab and 7Bb, respectively. An inlet chamfer 10 is provided at the open end of the outer joint member 2. Further, as shown in FIG. 7b, on the spherical outer peripheral surface 8 of the inner joint member 3,

track grooves

9A and 9B inclined in the circumferential direction with respect to the joint axial line NN (not shown) are alternately formed. The inclination directions of the

track grooves

9A and 9B are opposite to each other. The

track grooves

9A and 9B are composed of first track groove portions 9Aa and 9Ba and second track groove portions 9Ab and 9Bb, respectively.

FIG. 8 shows a front drive shaft 20 of an automobile incorporating the fixed type constant velocity universal joint 1 according to the first embodiment of the present invention. The fixed type constant velocity universal joint 1 is connected to one end of an intermediate shaft 11, and a sliding type constant velocity universal joint (in the example shown, a tripod type constant velocity universal joint) 15 is connected to the other end of the intermediate shaft 11. Between the outer peripheral surface of the fixed type constant velocity universal joint 1 and the outer peripheral surface of the shaft 11 and between the outer peripheral surface of the sliding type constant velocity universal joint 15 and the outer peripheral surface of the shaft 11, bellows-

like boots

16 a and 16 b are provided. Are attached and fixed by boot bands 18 respectively. Grease as a lubricant is sealed inside the joint. Since the fixed type constant velocity universal joint 1 according to the present invention is used, a lightweight and compact automobile drive shaft 20 is realized that has low torque loss and heat generation, high efficiency, and a high operating angle.

The constant velocity universal joint 1 according to the first embodiment of the present invention has been described above. However, the constant velocity universal joint 1 can be variously modified without departing from the gist of the present invention. . Hereinafter, a constant velocity universal joint according to another embodiment of the present invention will be described. However, in the following, the configuration different from that of the first embodiment will be described mainly, and members / parts having the same functions as those of the first embodiment will be denoted by the same reference numerals and redundant description will be omitted.

FIG. 9 shows a cross-sectional view of a main part of a fixed type constant velocity universal joint according to the second embodiment of the present invention. This figure is a cross-sectional view of an outer joint member used by being incorporated in a fixed type constant velocity universal joint. More specifically, like FIG. 4, a plane including a ball track center line X and a joint center O of a track groove 7A. It is sectional drawing of the outer joint member seen by M (refer FIG. 2a). In the constant velocity universal joint of this embodiment, the second track groove portion provided in the track groove of the outer joint member and the inner joint member is curved in a straight portion and an arc portion (on the opposite side to the first track groove portion). The configuration is different from the constant velocity universal joint of the first embodiment described above in that it is formed of an arc-shaped portion.

Specifically, the curvature center Oo2 of the ball track center line Xb of the second track groove portion 7b of the outer joint member 2 is equal to the curvature center Oo1 of the first track groove portion 7a (the ball track center line Xa thereof) and the first track groove portion 7a ( The ball trajectory center line Xa) is moved from the straight line L1 connecting the opening side end A to the opening side by f2. Therefore, the linear portion (the back end portion) of the ball track center line Xb of the second track groove portion 7b is connected to the opening side end portion A of the ball track center line Xa of the first track groove portion 7a. The arc-shaped portion of the ball track center line Xb of the second track groove portion 7b is connected to the opening side end portion (point C). And although illustration is abbreviate | omitted, the track-track center line Y of the track groove 9 of the inner joint member 3 makes the track groove 7 used as the pair of the outer joint member 2 on the basis of the joint center plane P in the state of 0 degree of operation angles. Are formed in mirror image symmetry with the ball trajectory center line X.

FIG. 10 shows a cross-sectional view of a main part of a fixed type constant velocity universal joint according to a third embodiment of the present invention. This figure is a cross-sectional view of an outer joint member used by being incorporated in a fixed type constant velocity universal joint. More specifically, similar to FIGS. 4 and 9, the ball track center line X of the track groove 7A and the joint center are shown. It is sectional drawing of the outer joint member seen in the plane M (refer FIG. 2a) containing O. FIG. In the constant velocity universal joint of this embodiment, the center of curvature of the ball track center line of the first track groove portion provided in the track grooves of the outer joint member and the inner joint member is mainly open side with respect to the joint center O. In addition to being offset to the back side, the tilt axis (axis tilted in the circumferential direction with respect to the joint axis NN) is offset in the radial direction with respect to N′-N ′, and this The configuration of the ball track center line of the second track groove portion is adjusted to correspond to the configuration of the fixed type constant velocity universal joint according to the first embodiment described above.

More specifically, the center of curvature Oo1 of the ball track center line Xa of the first track groove portion 7a of the outer joint member 2 is offset to the opening side with respect to the joint center O and has a radius with respect to the inclined axis N′-N ′. The direction is offset by fr. That is, it is offset by fr in the radial direction on the joint center plane P in a state where the operating angle including the perpendicular K is 0 °. Accordingly, the position of the curvature center Oo2 of the ball track center line Xb of the second track groove portion 7b is adjusted so as to smoothly connect to the opening side end A of the ball track center line Xa of the first track groove portion 7a. . With this configuration, the depth of the track groove on the back side of the joint can be adjusted. Although not shown, the ball track center line Y of the track groove 9 of the inner joint member 3 is a ball of the track groove 7 that forms a pair of the outer joint member 2 with reference to the joint center plane P in a state where the operating angle is 0 °. It is formed mirror-symmetric with the orbit center line X.

FIG. 11 shows a cross-sectional view of a cage used in a fixed type constant velocity universal joint according to a fourth embodiment of the present invention. That is, the fixed type constant velocity universal joint of this embodiment is the first embodiment in that a cage in which the spherical outer peripheral surface and the center of curvature of the spherical inner peripheral surface are offset in the axial direction with respect to the joint center O is used. The configuration is different from that of the fixed type constant velocity universal joint.

More specifically, as shown in FIG. 11, the center of curvature Oc1 of the spherical outer peripheral surface 12 of the cage 5 is offset from the joint center O by the dimension f3 toward the opening side. The curvature center Oc2 is offset from the joint center O by a dimension f3 on the back side. With such a configuration, the thickness of the cage 5 gradually increases toward the opening side, and the strength of the cage 5 particularly at a high operating angle can be improved. As described above, in the range of the high operating angle, the balls 4 arranged in the circumferential direction are divided into the first track groove portions 7Aa, 9Aa (7Ba, 9Ba) and the second track groove portions 7Ab, 9Ab (7Bb, 9Bb). Temporarily separated. In this case, a force is applied to the opening side from the ball 4 positioned in the second track groove portions 7Ab, 9Ab (7Bb, 9Bb) to the pocket portion 5a of the cage 5, but the meat of the cage 5 moves toward the opening side. Since the thickness is gradually increased, the strength of the cage 5 can be improved. In addition, the depth of the track grooves 7 and 9 (first

track groove portions

7a and 9b) on the back side can be increased.

In the fixed type constant velocity universal joint according to the present invention described above, the number of the balls 4 is eight, but is not limited thereto. Although illustration is omitted, for example, the present invention can be preferably applied to a fixed type constant velocity universal joint in which the number of balls is 10 or 12.

Further, the fixed type constant velocity universal joint of the above-described embodiment is configured such that the second track groove portion (the ball trajectory center line Xb thereof) is configured by only an arc-shaped portion or a combination of an arc-shaped portion and a linear portion. It was supposed to be, but it is not limited to this. In short, any shape can be used as long as the shape is different from the ball track center line Xa of the first track groove portion and the effective track length can be increased to increase the operating angle. Or a straight line. In addition, either one or both of the first track groove portion and the second track groove portion may be formed not by a single arc-shaped portion but by a plurality of arc-shaped portions in consideration of the track groove depth and the like.

In the above, the case where the present invention is applied to a fixed type constant velocity universal joint in which track grooves are arranged at a constant pitch in the circumferential direction has been described. In addition, the present invention can be preferably applied. Further, in the fixed type constant velocity self-joint described above, the inclination angle γ of the track groove (first track groove portion) with respect to the joint axis NN is made equal in all the track grooves. However, the present invention is not limited to this. If the inclination angle γ of the track groove (first track groove portion) of the outer joint member and the inner joint member that make a pair (opposite in the radial direction) is equal, the mutual distance between the track grooves (first track groove portions) The inclination angle γ may be varied. In short, each inclination angle should be set so that the axial force of the ball acting on all the pockets in the circumferential direction of the cage is balanced as a whole. Further, in the above, the present invention is applied to the fixed type constant velocity universal joint configured such that the track groove and the ball are in contact with each other with an angle of contact (angular contact). However, the present invention is not limited to this, and the present invention is not limited to this. The present invention can also be preferably applied to a fixed type constant velocity universal joint in which the cross-sectional shape of the groove is formed in an arc shape and the track groove and the ball are in circular contact.

The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the scope of the present invention. The scope of the present invention is not limited to patents. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

1 Fixed type constant velocity universal joint (constant velocity universal joint)
2 outer joint member 3 inner joint member 4 ball 5 cage 6 spherical inner peripheral surface 7 track groove 7a first track groove portion 7b second track groove portion 8 spherical outer peripheral surface 9 track groove 9a first track groove portion 9b second track groove portion 12 spherical shape Outer peripheral surface 13 Spherical inner peripheral surface 20 Drive shaft A Open side end B Back side end K Perpendicular line L1, L2 Straight line M Flat surface including ball track center line N Joint axis N 'Inclined axis O Joint center P Joint center plane Q Plane R1, R2 including the ball trajectory center line Straight line X Ball trajectory center line Y Ball trajectory center line γ Inclination angle β Angle θ Operating angle

Claims

A plurality of track grooves extending in the axial direction are formed on the spherical inner peripheral surface, and an outer joint member having an opening side and a back side that are separated in the axial direction, and a plurality of pairs that form pairs with the track grooves of the outer joint member on the spherical outer peripheral surface An inner joint member formed with a track groove, a plurality of balls that are interposed between the track groove of the outer joint member and the track groove of the inner joint member, and that transmit the torque; In a fixed type constant velocity universal joint comprising a spherical inner peripheral surface of a joint member and a spherical outer peripheral surface and a cage having a spherical inner peripheral surface that are fitted to the spherical outer peripheral surface of the inner joint member, respectively.
The track groove of the outer joint member includes a first track groove portion located on the back side and a second track groove portion located on the opening side, and the first track groove portion is offset to the opening side with respect to the joint center. The first track groove portions adjacent to each other in the circumferential direction are inclined in the circumferential direction with respect to the joint axis, and are inclined in the opposite directions to each other. The track groove has a shape different from that of the first track groove in order to increase the effective track length with respect to the maximum operating angle, and is connected to the first track groove on the opening side from the joint center,
The track groove of the inner joint member is formed in a mirror image symmetry with the track groove forming a pair of the outer joint member with respect to a joint center plane at an operating angle of 0 °. Universal joint.
The angle β formed by the straight line connecting the point where the first track groove portion and the second track groove portion are connected to the joint center is set to 3 ° to 10 ° with respect to the joint center plane in the state where the operating angle is 0 °. The fixed type constant velocity universal joint according to claim 1, wherein the fixed type constant velocity universal joint is provided.
The fixed constant velocity universal joint according to claim 1 or 2, wherein the center of curvature of the first track groove portion is arranged on an inclined axis inclined in a circumferential direction with respect to an axis of the joint.
3. The fixed type according to claim 1, wherein the center of curvature of the first track groove is disposed at a position offset in a radial direction with respect to an inclined axis inclined in a circumferential direction with respect to an axis of the joint. Constant velocity universal joint.
The center of curvature of the spherical outer peripheral surface of the cage is arranged at a position offset to the opening side with respect to the joint center, and the center of curvature of the spherical inner peripheral surface of the cage is offset to the back side with respect to the joint center. The fixed type constant velocity universal joint according to any one of claims 1 to 4, which is disposed at a position.
The second track groove portion has an arcuate portion having a center of curvature at a position that is radially outward of the first track groove portion and offset toward the opening side from the joint center. The fixed type constant velocity universal joint as described in any one of the above.
The fixed type constant velocity universal joint according to claim 6, wherein the second track groove portion includes only the arc-shaped portion, and the arc-shaped portion is smoothly connected to the first track groove portion.
The fixed type according to claim 6, wherein the second track groove portion includes the arc-shaped portion and a linear portion, and the linear portion is smoothly connected to the first track groove portion. Fast universal joint.
The fixed type constant velocity universal joint according to any one of claims 1 to 8, wherein the number of the balls is 8, 10, or 12.